Motor compressor



,Jan. 14, 1936. R. PA'fERAS PESCARA ,0 7,877

MOTOR COMPRES 8 OR Filed Feb. 23, 1955 4 Sheets-Sheet 1 Jan. 14, 1936 R. PATERAs PESCARA 2,027,877

' v I MOTOR COMPRESSOR- Filed Feb. 2a, 1935 4 Sheets-Sheet 2 V 5 n r'.\ R

Jan. 14, 1936. R. PATERAS PESCARA 2,027,877

MOTOR COMPRESSOR Filed Feb. 23,1935 I 4 Sheets-Sheet 3 Jan. 14, 1936.

R. PATEIRAS PESCARA MOTOR COMIRESSOR Filed Feb. 25/1953 ,4 Sheets-Sheet 4 In V612 for fl Horn 4 that Jan. M, 193

moron cotmnrssoa lltaul llateras Fescara, Paris, France Application February 23, 1933, Serial No. 65$,l'iiin France February 23, 11932 30 Claims.

10 while the outer faces of the two pistons recipro cate in two separate cylinders respectively and serve to compress the air therein. The chief problem in connection with compressors of that type is to insure a satisfactory return or inl5 -'ward stroke of the pistons in spite of possible variations in the length of the outward stroke.

The object ofthe present invention is to provide. a motor compressor of that type in which variations in the length of the outward stroke are not detrimental to a satisfactory running of the compressor.

The motor compressor according to my invention comprises at least two simple compressors of the type above referred to, the two pairs of pistons of which are respectively coupled together through positive means so that the outward stroke of one pair of pistons is made 130] control the inward stroke of the other pair. In that way the energy for the return stroke of one pairof pistons is equalto the sum of the energy-stored in the air compressed in the dead spaces of the compressing cylinders of said pair of pistons and of the energysupplied by the explosive mixture between the pistons of the other pair. Such a motor compressor is adapted to work within a certain range of values of said energy.

Accordingto my invention, the simple compressors-are'so devised as to meet the two fol- 4 lowing conditions: I

(a) When the energy for the return stroke of one pair of pistons, that is tosay when the sum of the energy stored in the air compressed in the compressing cylinders of said pair of pistons, and ofthe energy of the explosive mixture present between the pistons of the other pair falls to its lowest admissible value, an accidental decrease in the length of stroke of the pistons causes the energy of the explosive mix- .ture to decrease by an amount at most equal to that by which the energy stored in the compression cylinders increases.

(b) When the energy for the return strok reaches its highest admissible value, an acciden- 55 talincrease in the length of stroke of the pistons causes said energy of the explosive mixture to increase by an amount at most equal to that by which decreases the energy stored in the compression cylinders of the other pair of pistons.

Other characteristics of my invention will appear from the following description.

. Preferred embodiments of my invention will be hereinafter described with reference to the accompanying drawings, given example, and in which:

Fig. 1 is a diagrammatical view showing in longitudinal section a motor compressor having two pairs of pistons according to my invention;

Fig. 2 is a diagram of the. compression exerted by the outer faces of the pistons;

Fig. 3 is a diagram of the variations of pressure in the combustion chamber between two v pistons;

Fig. 4 is a diagrammatical view showing in longitudinal section' another embodiment of a motor compressor having two pairs of pistons according to my invention;

Fig. 5 is a similar view of still another, em-

bcdiment;

Fig. 6 is a longitudinal section ofa motor compressor having three pairs of pistons according to my invention;

Fig. '7 is a side view of the partly cut away;

Fig. 8 is a diagrammatical view of a motor compressor unit provided with an automatic adjusting device;

Fig. 9 is a diagrammatical view of a similarmotor compressor unit provided with another automatic adjusting device;

Fig. 10 is a diagrammatical view of a motor compressor unit provided with still another automatic adiusting device;

Fig. 11 is ,a diagrammatical view of a motor unit consisting of two simple motor compressors and provided with asafety stop device. The motor compressor of Fig. 1 comprises four pistons, I, 2, 3, ands. Pistons II and 2 reclprocate on the one hand both in cylinder 5 which 45 is the .power cylinder, and on the other hand in cylinders 6 and ll-respectively, which are the air compression cylinders. In a like-wise manner, pistons 3 and 4 reciprocate on the one handboth in cylinder 8 and on the other handeach in cylinders 9 and it) respectively. Pistons 2 and 3 are connected together by a rack ll.

Rack Ii meshes with two pinions which, on. the other hand, mesh with tworacksflfl! respectively. Toothed pinions. l2 aspe -1e by an 55 device .of Fig. 6,

merely by way of 10 35 pistons tend to move with diflerent speeds.

equalizing bar l3 pivoted about axis 45. Racks I4 are carried by rods I5 and I6 which connect pistons I and 4, together.

The cycle in cylinders 5 and 8 takes place in 5 the known manner for two stroke engines with opposed pistons in which the scavenging is effected through suitably disposed ports. Pistons I and 2, which in the drawings are shown at or near the inner ends of their stroke, are driven 10 apart by the combustion of the fuel in cylinder 5. They impart their movement, through rods I5 and I6 and rack II, to pistons 4 and 3 respectively and bring said pistons back toward eachother until, due to ignition of the fuel in cylinder 8, the outward stroke'of said pistons- 3 and 4 takes place, which then drives pistons I and 2 back toward each other. During the outward stroke of pistons I and 2, air is compressed in cylinders 6 and I, from which it passes, through suitable valves into a compressed air storage tank. The compressed air cushions remaining in the dead spaces of said compression cylinders 6 and I also help in driving pistons I and 2 during the inward stroke thereof. In a likewise manner, the air remaining in the dead spaces of compression cylinders 9 and It) also helps in bringing pistons 3 and 4 back to their inner positions.

Pinions I2, which mesh with rack II on the one hand and racks I4 respectivelyon the other It results from the above described operatic that the energy for the return stroke of, say,

pistons I and 2 results from both the compression of air in the dead spaces of cylinders 8 and 1 and the combustion of the explosive mixture in cylinder 8. It will now be shown how, ac-

cording to applicants arrangement, said energy for the return stroke of pistons I and 2 meets the conditions above stated. This will be better understood by referring to the diagrams of Figs. 2 and 3. It will be supposed that Fig. 2

shows the variations of pressure in chambers 6 and 1. The pressures are plotted in ordinates and the lengths of stroke in abscissas. As for Fig. 3 it shows the variations of pressure in chamber 8. The pressures are plotted in ordi- 56 nates and the lengths of stroke in abscissas. As pistons 2 and 3 and pistons I and 4 are regidly connected together, their linear displacements are exactly equal. graphs of Figs. 2 and 3 have been placed exactly 60 over each other so that their abscissas may correspond.

If it be supposed that the length-of the ou ward stroke of pistons I and 2 is ai (Fig. ,2) an therefore that the length of the inward stroke ofpistons 3 and 4 is no (Fig. 3), equal to db,

then the diagram of pressures in chamber I will be abcd (Fig. 2), while the diagram of pressures in chamber 8 will be nopm (Fig. 3). It follows that the energy for the return of pistons I and 2 will be proportional to the sum of the areas icd (Fig. 2) andnvpm (Fig; 3).

the ordinates have been plotted on different scales 'in the graphs of Figs. 2 and. 3 so as to take into account, and compensate for, the

differences in the areas of the piston faces on Consequently, the

Of course,

As in all two stroke engines of this type, the

cycle in motor cylinder 5 is such as to allow for a certain range of variations of that energy for the return of pistons I and 2, the lowest admissible value of that energy being that which corresponds to a heating of the combustion air sufficient for igniting the fuel at the end of the compression stroke, and the highest admissible value of that energy being that above which the apparatus might risk to be injured.

These limits being fixed, according to my invention, I choose the dimensions of the compressor elements (bores of the cylinders, dead spaces of the air compression cylinders) in such manner that, when the energy for the return of one pair of pistons falls to its lowest admissible value, an accidental decrease of the stroke of the (pistons is not capable of further reducing said energy, and when the energy for the return of one pair of pistons reaches its highest admissible value, an accidental decrease of the stroke of the pistons is not capable of further increasing said energy.

Thus, if, in the diagrams of Figs. 2 and 3, the length of stroke ai (Fig. 2) and m) (Fig. 3) is supposed to correspond to the lowest admissible energy for the return 01', pistons I and 2, it there occurs an accidental reduction of said length of stroke so that it becomes ak (Fig. 2) (nu in Fig. 3), the new diagrams of pressures will be abef (Fig. 2) in cylinders 8 and 1 and nrqm (Fig. 3) in cylinder 8. The energy for the return of pistons I and 2 will therefore be proportional to the sum of the areas kef (Fig. 2) and nuqm (Fig. 3).

According to my invention, the dimensions of the various elements of the compressor are so chosen that that sum is at least equal to the sum of areas icd and nvpm corresponding to the case of a stroke of the pistons equal to or (and no). This is due to the fact that, it area nuqmis smaller than area nvpm, on the contrary area he! is larger than area icd, and the dlflerence between areas nvpm and nuqm is at most equal to the difference between areas kef and'icd. On the contrary, if, in the diagram 01' Fig. 2 and 3, the length of stroke ai (Fig 2) and no (Fig. 3) is supposed to correspond to the highest the return oi pistons I and 2 will therefore be proportional to the sum of areas nwSm (Fig. 3)

and egh (Fig. 2).

. According to my invention, the dimensions of I the various elements of the compressor are so chosen that said sum is at most equal tothe sum of areas icd and nvpm corresponding to the case of a stroke of the pistons equal to ai (and 1m). This is due to the fact that, if area nwSm is larger than area nvpm, on the contrary area call. is smaller than area fed, and the difference.

-pinions 50, 5| respectively. 40

keyed.

device is similar to that of the deviceof Fig. l.

aoeaew through variation of the injection of fuel. It is possible to run under half load by causing one of the simple compressors to run idle by opening the valvesof the compressing cylinders combustion chambers 'of said cylinders are 25,

fit respectively, while the compression chambers are'2'll, 28 and 29, 30 respectively. Pistons 2i and 2d are connected together through a rod ti, and pistons 22 and 23 are connected together through a rod 32. Pistons 22 and M are provided respectively with rods 33 and it which project outwardly from the cylinders and are 'connected through cranks 35 and lit with an equalizing bar 38 pivoted about axis 31!.

The operation of such a device is obviously similar to that described with reference to Fig.

l. Rods 3i and 32 play the parts of rack Ill on the one hand and rods i5 and it on the other hand. The movements of the two pairs of pistons are synchronized by equalizing bar M.

In the embodiment of Fig. 5 the pistons and cylinders are disposed as in the embodiment of Fig. 4. The connection between the two pairs of pistons is furnished by piston rods 39, M, til, M which project from both ends of the cylinders and are connected through cranks ttwith equalizing bars 46, M pivoted about axes M, M respectively. Said equalizing bars are provided with toothed sectors t8 and M which mesh with bevel Said pinions are connected through a shaft 52 on which they are In this case also the operation of the Levers t6 and ll, together with the piston rods connected thereto, play the parts of rack ill and rods i5 and it of the embodiment of Fig. 1.

Toothed sectors 48, M with their co-operating pinions 59,5! play the part of pinions 02 of the embodiment of Fig. 1. g

I may also, as shown in Fig. 6, apply the principle of my invention to the case of a compressor having more than two pairs of pistons. In the embodiment of Fig. 6, the compressor comprises three pairs of pistons, 535t, 5t-5l and 5t5li. Pistons 53 and 55 are connected with each other and with piston 51 through bent rods 59 provided with racks 6i. Pistons 56 and 58 are connected with each other and with piston 5t through'bent rods til provided with racks t2.

Racks ti and 62 mesh with pinions t3 carried by the compressor casing or frame. In this case the outer stroke of the'two outer pairs of pistons corresponds to the inward stroke: of only one pair of pistons, namely 54-51 On the contrary, the outward stroke of the last mentioned'pair of v pistons corresponds to the inward stroke of'the two'other pairs of pistons. The advantage-of that embodiment lies in the symmetry of the elements for connecting together the several pairs" of pistons.

Of course, in the embodiments of Figs. 4, 5

and 6, the conditions concerning the dimensions of the elements of the compressor are the same as above explained concerning the embodiment of Fig. 1', so that accidental variations in the lengths of stroke .of the pistons may be corrected as above explainedwith reference to Figs. 2 and 3. i

Another very important problem relating to motor compressors of the type above referred to, is to regulate the amount of fuel fed to the power cylinders according to the circumstances under which the machine is working. and in particular when the compressor is being started. Otherwise, due to the rapid increase of the energy resulting from the rate of compression of the air in the power cylinders, the machine might be very quickly injured, for instance by the power cylinders bursting.

The regulating means that are already known and applied to simple motor compressors of the type with which my invention is concerned, are adapted to proportionate the amount of fuel fed to the power cylinders to the output of compressed gas that is produced. Said means are hardly applicable to multiple motorcompressors,

for instance to motor compressors consisting of two simple motor compressors coupled together since the variations of output of the compressors are very small because the variation of the length of stroke of the pistons are themselvesnecessarily very limited.

One object of my invention is to provide a system of regulating multiple motor compressors of the type above referred to.

a According to a first embodiment the feed of the various injection pumps is adjusted according to the exhaust pressure (which is very low when the machine is being started) so that said feed diminishes when that pressure decreases. Furthermore, I preferablydispo'se on the outlet pipe of the multiple motor compressors, a throttling valve ll which is sensitive to variations of the pressure existing in front of said organ, so that when said pressure rises above a determined maximum, the valve is closed thus shutting off said pipe and directing the discharged gases toward'the atmosphere, or toward a chamber in which the pressure is relatively low.

Such an arrangement is shown in Fig. 8 which shows a motor compressor consisting of two simple or elementary compressors A and 18,

coupled together as above described. These simple or elementary compressors are fed through injection pumps I133 and Mt, comprising regulatingrods I35, I36 respectively.

Said rods are connected, through suitable mechanical means, to an organ sensitive to the pressure existing .in outlet main i3 1, so that when said pressure is low the amount of fuel that is fed may be small, and on the contrary when that said pressure is high, the amount of fuel fed to the power cylinders is relatively;

throttle valve illadapted to operate as above explained. That throttle valve may consist for instance of a cylinder MI, in which move two pistons M2 and 3 connected to each other through a rod I, and pushed by suitableelastic means against a stop Hil The face of piston I42 that is located on the side of said stop is connected with reservoir I40. Three ports I45, I46 and I41 are provided in the wall of cylinder I4I, so that port I45 communicates with reservoir I40, port I46 communicates with main I31 and port I41 communicates with the atmosphere. The whole is so arranged that port I46 is always located between pistons I42 and I43 whatever their position may be. On the other hand when the pistons are in contact with stop I4I port I45 is located between the pistons and port I4! is covered by piston I43. Finally when the pistons have moved against the action of the elastic means, port I45 is covered by piston I42.and port I4! is located between the pistons.

The elastic means above referred to advantageously comprise on the one hand a spring I48 that constantly pushes the piston toward stop I4I and on the other hand at least two springs I49, I50 pivoted to fixed points so that said springs acting alternately in the direction of spring I48, and in the opposite direction, make it possible to automatically obtain a more rapid working of the valve.

This multiple motor compressor operates as follows:

If the pressure in reservoir I40 rises above a certain value, throttle valve 0 connects the outlet pipe I31 of the compressor with the atmosphere, and the piston I39 of the fuel regulating system displaces regulating rods I and I36 so that these rods diminish the quantity of fuel fed into the power cylinders.

On the contrary, if the pressure in reservoir I falls below a certain value, the valve establishes a connection between outlet pipe I31 and said reservoir I40 and according to the value of the-exhaust pressure which may be equal to zero, especially when the machine is being started, piston I39, subjected to a force proportional to said pressure, acts in a suitable manner on the control rods of the feed pumps.

According to another embodiment of my invention, the feed regulating means and the outlet slide valve as described with reference to the preceding embodiment, are connected with only some of the simple or elementary motor compressors. The means for feeding fuel into the other simple or elementary motor compressors depend directly on the pressure existing in reservoir I40 fed by the machine.

Owing to this arrangement, it will be under- 7 stood that when the first mentioned elementary compressors are caused to run idle by the action of throttle valve 0 the other elementary compressors may work as ordinary simple motor compressors, the compensating cushions of which will be furnished by the power cylinders of the first mentioned elementary compressors.

The latter may then work under any working conditions .between the running'under no-load .and the running under their full load, which corresponds to the half load of the complete machine-if said machine comprises an even number of elementary compressors.

Such an arrangement is disclosed in Fig. 9 which shows a motor compressor consisting of two elementary compressors A and .B.

A throttle valve 0 similar to that above -described, isinserted between the exhaust main The exhaust main I52 of elementary compres sor A is directly connected to reservoir I40. The feed of fuel to said elementary compressor A is regulated through a device (comprising for instance a cylinder I53 and a piston I53 sensitive to the variations of the pressure existing in reservoir I40.

Advantageously throttle valve 0 is adjusted in such manner that it connects main I5I with the atmosphere for all the pressures that are higher than a certain limit. Above said limit, the amount of fuel fed by pump I34, which is regulated bythe action of the organ I38, I39 sensitive to the variations of the pressure in main III, is equal to zero or extremely small. The power cylinder of elementary compressor 13 then acts as a compensating cushion adapted to cooperate 'with elementary motor compressor A. As for the air compression cylinders of elementary compressor B, they take up and give back an insignificant energy, because they are in communication with the atmosphere.

The element I53, I53"- for regulating the feed of fuel to elementary compressor A, the exhaust main I52 of which is constantly in communication with reservoir I40, is so adjusted that on the one hand below the limit pressure above which the throttle valve .0 causes elementary compressor B to run idle, the amount of fuel fed by pump I33 increases with the pressure existing in said reservoir, and this preferably according to the same law as for pump I34, but on the other hand, above said limit pressure, the amount'of fuel fed by pump I33 decreases when the pressure further increases in reservoir I40, that is to say when the need of compressed air diminishes until the maximum pressure is reached in said reservoir and elementary compressor A itself runs idle.

Although the regulating element acts always in the same direction on the rod I35 of pump I33, 9. special arrangement of said pump will make it possible to obtain the desired result, to wit, that from a certain pressure up the amount of fuel fed by pump I33 must decrease, although, as a result of the still increasing pressure, rod I35 still moving in the same direction.

To this effect according to my invention, I cause rod I35 to control by a cam of such an outline that from said limit pressure up the variation of feed of pump I33 may be reversed.

A third embodiment of the regulating device for multiple motor compressors according to my invention is more particularly adapted to be applied to machines of that kind for operating a receiving device without the addition of an intermediate reservoir. The chief feature of this embodiment is to provide the receiving device with a governor R which is connected with a distributing valve for controlling the inflow of the motive fluid to the receiving device, so that the pressure of said fluid and therefore the discharge pressure of the'motor compressor vary in accordance with the speed of the receiving device, so as to decrease when said speed itself decreases. Furthermore, means are provided for varying the amount of fuel fed to the motor compressor in accordance with said exhaust pressure, so that the feed decreases when said pressure itself decreases.

Such an arrangementv is' disclosed in Fig. 10, which shows a turbine having four stages, I54, I55, I53 and I51. A distributing element is so arranged that according to the position of a slide valve I54, exhaust main I of the motor comtil laoavgevv pressor is connected with one or the other of the four stages of the turbine. To this eflect slide valve it may consist of a sliding member provided with four ports it, iii, ltd and ltd adapted to coactwith conduits tilt, ltd," ltd and it'll respectively connected to the four stages of the tubine so that when the slide valve is moved iiuid' is fed into the high pressure stage, and

then, as the speed of revolution increases successively toward stages of decreasing pressure.

Adnantageously, insteadof positively connecting said sliding valve with centrifugal governor it, these elements are elastically connected together, for instance through a spring ltd, and slide valve i518 is so arranged (for instance by providing it with a piston E69 subjected to the exhaust pressure) that said spring may be the more compressed as said pressure is higher. Thus the passage from one stage to the next stage of lower pressure is delayed if the exhaust pressure is higher than the mean pressure, and

is advanced if that pressure is smaller than it.

Finally, I provide means as above described for regulating the fuel feed, which may consist for instance of cylinder ill] and a piston El, sensitive to variations of the pressure existing in main ltd.

Owing to this arrangement if the load under which the turbine is running tends for instance to decrease, the rotor tends to revolve fasterj governor R acts on slide valve i583 so that the compressed fluid instead of entering the receiver through the high pressure stage ill t, enters through a stage of lower pressure. This produces an immediate decrease of pressure in the exhaust main, and therefore under the action of regulating organ H0, ill, decreases the amount of fuel fed to the power cylinders.

Of course a reverse action (increase of the load under which the turbine runs) would bring a reverse variation of the feed of the pumps.

It should be noted that the receiver may be of any kind whatever, either staged or not, either rotary or not. In particular it might quite well consist of a piston machine, for instance" of the compound type. 1 n

Whatever be the embodiment that is chosen, I advantageously fit the motor compressor of the type above described with a safety device adapted to stop the enginewhen the length of stroke of the pistons reaches the n aximum admissible for the machine. .Such an arrangement is shown in Fig. ll in which the two-pistons l and t of a given elementary compressor are connected through rods E2, it jointed to the ends of an oscillating lever it controlling feed pumps ltd, itt through elements such as cams it of suitable outline.

The angles of oscillation are so' chosen that when said rods move beyond their cinematic dead centre, which corresponds to a value of the length of stroke equal to the upper limit thereof, they bring the oscillating lever into a new angular zone in which at least one of the cams ceases to act on the corresponding ele ments for controlling the feed pumps so that the machine is then immediately stopped.

While I have described whatI- deem to be practical andefiicient embodiments of my invention, it should be well understood that I do nu. wish to be limited thereto as there might be changes made in the arrangement, disposition andform of the parts without departing from.

the principle of my invention as comprehended within the scope of the appended claims.

What I- claim is: I 1. A motor compressor of the type described comprising in combination, at least two power cylinders, at least two pairs of opposed pistons adapted to reciprocate in said cylinders respectively, means for feeding fuel into said cylinders, at least two pairs of compression cylinders adapted to receive the outer ends of said two pairs of pistons respectively, connecting means between the pistons of said two pairs respectively for causing the outward stroke of one pair to imperatively control the inward stroke of the other pair, the dimensions of said parts being so chosen that, when the sum of the energy of the explosive mixture in one power cylinder and of the energy stored in the fluid compressed at the end of the compression stroke in the compression cylinders corresponding to the other cylinder falls down to its lowest admissible'value, an accidental decrease in the length of stroke of the pistons causes said energy of the explosive mixture to decrease by an amount at most equal to that by which the energy stored in said compression cylinders decreases, and when said sum reaches its highest admissible value an accidental increase in the length of stroke of the pistons causes said energy of the explosive mix--- ture to increase by an amount at most equal to that by which the energy stored in said compression cylinders decreases. w

2. A motor compressor of the type described comprising in combination, two power cylinders in line with eachother, two pairs of opposed pistons adapted to reciprocate in said cylinders respectively, two pairs of compression cylinders disposed on opposite sidesof the firstmentioned cylinders respectively and adapted to receive the outer ends of the pistons of said first mentioned cylinders respectively, and means for rigidly connecting one piston of one pair to the opposite piston of the other pair.

3. A motor compressor of the type described comprising in combination, two power cylinders in line with each other, two pairs of opposed pistons adapted to reciprocate in said cylinders respectively, two pairs or compression cylinders disposed on opposite sides of the first mentioned cylinders respectively and adapted to receive the outer ends of the pistons of said first mentioned cylinders respectively, a rod for rigidly connecting together the two adjacent pistons of the two pairs respectively, two rods, one on each side of the first mentioned rod, for rigidly connecting together the two other pistons or said pairs respectively, two racks, one on each side of the first mentioned rod, facing the two second mentioned rods respectively, a rack on one side of each of the two second mentioned rods facing one of the two above mentioned. racks respecf tively, anequalizing lever pivoted about a central axis at right angles tojt'he plane of said three rods, two pinions pivoted on said lever on either side of said axis andadapted to mesh each on the one hand with one rack of the first mentioned rod and. on the other hand with the raclt of one of thetwo other rods.

4. A motoncompressor of the type described, comprising in combination, two power cylinders! disposed side by side, two pairs of opposed pis tons adapted to reciprocate in said cylinders respectively, two pairs of compression cylinders disposed on opposite sides of the first mentioned cylinders respectively and adapted to receive the outer ends of the pistons of said first mentioned cylinders respectively, two rods each articulated at one end to one of the pistons of one pair and at the other end to the opposite piston of the other pair, two rods rigidly fixed to adjacent pistons of the two pairs respectively projecting outwardly from the outer ends of the corresponding compression cylinders, and an equalizing bar pivoted about a fixed axis and articulated at both ends with the two last mentioned rods respectively.

5. A motor compressor of the type described, comprising in combination, two power cylinders disposed side by side, two pairs of opposed pistons adapted to reciprocate in said cylinders respectively, two pairs of compression cylinders disposed on opposite sides of the first mentioned cylinders respectively and adapted to receive the outer ends of the pistons of said first mentioned cylinders respectively, two rods, substantially coaxial with said cylinders respectively, rigidly fixed to the adjacent pistons of the two pairs respectively and projecting outwardly from the outer ends of the corresponding compression cylinders, two other rods, substantially coaxial with said cylinders respectively, rigidly fixed to the other adjacent pistons of the two pairs respectively and projecting outwardly from the outer ends of the corresponding compression cylinders, two levers pivoted about axes at right angles to the common plane of the two cylinders, each lever being articulated at both ends with the outer ends of said two pairs of rods respectively, a toothed sector carried by each of said levers, a shaft extending longitudinally between the two cylinders, and toothed means keyed at each end of said shaft for engaging said toothed sectors respectively.

6. A motor compressor of the type described comprising in combination, at least three parallel cylinders disposed side by side, a pair of pistons adapted to reciprocate in each of said cylinders, three pairs of compression cylinders disposed on opposite sides of the three first mentioned cylinders respectively, rigid means for connecting together one piston of the central cylinder with both of the two opposite pistons of the outer cylinders, rigid means for connecting together the other piston of the central cylinder with both of the two opposite-pistons of the outer cylinders, and equalizing means between the two-last mentioned means for synchronizing the movements of the two groups of three pistons.

'l. A motor compressor of the type described, comprising in combination, three parallel cylinders disposed side by side, a pair of pistons adapted to reciprocate in each of said'cylinders,

three pairs of compression cylinders disposed on opposite sides of the three first mentioned cylinders respectively, rigid means for connecting to gether one piston of the central cylinder with both of the two opposite pistons of the outer cylinders respectively, rigid means for connecting together the other piston of the central cylinder 'with-both of the two opposite pistons of the outer cylinders respectively, a rack carried by the first mentioned rigid means, another rack, facing the first mentioned one, carried by the second mentioned rigid means, and a pinion, iournalled about a fixed axis with respect to the cylinders, in mesh with both of said racks.

8. A compressor according to claim 7 in which the axes of the three first mentioned cylinders are in the same plane, the two racks and cooperating pinion being all disposed on one side of said plane, the compressor further comprising a similar system of two racks and a cooperating pinion symmetrically disposed on the other side of said plane.

9. A motor compressor of the type described comprising in combination, at least two power cylinders, at least two pairs of opposed pistons adapted to reciprocate in said cylinders respectively, feeding means for injecting fuel into said alternately to said reservoir or to the atmosphere according to the pressure in said reservoir, and means sensitive to the pressure in said pipe for controlling the feeding means of the power cylinders corresponding to the last mentioned compression cylinders.

10. A motor compressor according to claim 9 in which the means for co ecting said pipe alternately to said reservoir or to the atmosphere comprises, a cylinder provided at one end with a port connected with said reservoir, at the other end with a port connected to the atmosphere, and in its intermediate part with a port connected with said pipe, two pistons rigidly connected together adapted to slide in the last mentioned' cylinder, and elastic means for urging said pistons toward the position for which the first mentioned port is covered by one of the pistons.

11. A motor compressor according to claim 9 in which the means for. controlling the feeding means comprises, at least one rod for regulating said feeding means, a cylinder connected at one end with said outlet pipe, and a piston in the last mentioned cylinder operatively connected with said rod.

12. A motor compressor of the type described comprising in combination, at least two power cylinders, at least two pairs of opposed pistons adapted to reciprocate in said cylinders respectively, feeding means for injecting fuel into said cylinders respectively, at least two pairs of compression cylinders adapted to receive the outer ends of said two pairs of pistons respectively, and connecting means between the pistons of said two pairs respectively for causing the outward stroke of one pair to imperatively control the inward stroke of the other pair, a reservoir, a main outlet pipe for connecting the whole of said ,pairs of compression cylinders to said reservoir, means provided on said pipe and sensitive to the pressure in said reservoir for connecting said pipe alternately to said reservoir or to the atmosphere according to the pressure in said reservoir, and means sensitive to the pressure in said pipe for controlling said feeding means. 1

13. A motor compressor of the type described comprising in combination, at least two power cylinders, at least two pairs of opposed pistons adapted to reciprocate in said cylinders, respecaustere tively, feeding means for injecting fuel into said Cylinders respectively, at least two pairs of compression cylinders adapted to receive the outer ends of said two pairs of pistons respectively,-

connecting means between the pistons of said two pairs respectively for causing the outward stroke of the other pair, a reservoir, at least two outlet pipes for connecting said pairs of compression cylinders to said reservoir respectively, means provided on some of said pipes and sensitive to the pressure in said reservoir for connecting the last mentioned pipes alternately to said reservoir or to the atmosphere according to the pressure inysaid reservoir, and means sensitive to the pressure in said pipe for controlling the feeding means of the power cylinder corresponding to the last mentioned compression cylinder.

14. A motor compressor according to claim 13, further comprising a means sensitive to the pressure in said reservoir for controlling the feeding means of the other power cylinders.

15. A motor compressor according to claim 13, further comprising a means sensitive to the pressure in said reservoir for progressively reducing the amount of fuel supplied by the feeding means of the other power cylinders when the pressure in said reservoir is above the limit for which the above mentioned pipes are connected to the atmosphere.

16. A motor compressor of the type described lcomprising in combination, at least two power -cylinders, at least two pairs of opposed pistons adapted to reciprocate in said cylinders respectively, feeding means for injecting fuel into said cylinders, at least two pairs of compression cylinders adapted to receive the outer ends of said two pairs of pistons respectively, and connecting means between the pistons of said two pairs respectively for causing the outward stroke of one pair to imperatively control the inward stroke of the other pair, a receiving machine adapted to be operated by the fluid under pressure from said compressor, a speed governor coupled to said machine, an dutlet pipe for conveying the fluid under pressure from said compression cylinders to said machine, distributing means in said pipe operatively connected to said governor for controlling the inflow of fluid to the machine so-that the pressure of the fluid decreases when the working speed of the ma- I chine itself decreases, and means sensitive to said pressure for controlling saidfeeding means creases. V

17. A device according to claim .16 in which said machine consists of a turbine having several stages, the distributing means being adapted to direct the fluid to the high pressure stage when theworkingspeed of the turbine is low and successively to lower and lower stages of pressure as said speed increases.

18. A motor-compressor comprising motor and Compression cylinders, at least'two pairs of pistons adapted to reciprocate in'said cylinders,

'and'means connecting said pairs of pistons to forcethe'pistons. of one pair to approach each other as those of the other pair move apart,

said compression cylinders having dead spaces therein, the size 6f the motor cylinders and of the dead spaces .in the compression cylinders being so chosen that a decrease in the energy developed in the motor cylinder of either pair of pistons is accompanied by an increase in the.

energy stored in the dead spaces of the cylinders of the other pair of pistons, while an increase inthe energy developed in the motor cylinder of either pair of pistons is accompanied by a decrease in the energy stored in the dead spaces of the cylinders of the other pair, where-- adapted to reciprocate in said cylinders respectively, two pairs of compression cylinders disposed on opposite sides of the first mentioned cylinders respectively and adapted to receive the outer ends of the pistons of said first mentioned cylinders respectively, a rod for rigidly connecting together the two adjacent pistons of the two pairs respectively, a rod on one side of the first mentioned rod forflrigidly connecting together the two other pistons of said pairs, a rack on one side of the first mentioned rod facing the second mentioned rod, a rack on one side of the second mentioned rod facing the above mentioned rack, an equalizing lever pivoted about a central axis at right angles to the plane of said rods, a pinion pivoted on said lever on one side of said axis and adapted to mesh with said racks.

20. A motor compressor of the type described comprising in combination, a power cylinder and a pair of opposed pistons adapted to reciprocate in said cylinder, means to feed fuel to said cylinder, an equalizing lever for synchronizing the movements of said pistons, and a cam integral with said lever for controlling said feeding means, all the parts being so arranged that when the pistons reach their outermost positions the said lever is brought into an angular position for which said cam is in inoperative position.

21. A motor compressor, comprising in combination, a power cylinder and a pair of opposed pistons adapted to reciprocate in said cylinder, means to feed fuel to said cylinder, a single equalizing lever for synchronizing the movements of said pistons, a plurality of cams all carried by said lever for controlling said feeding means, all the parts being, so arranged that when the pistons reach their outermost position the said lever is brought into an angular position for which at least one of said cams is in inoperative position.

22. A motor compressor consisting of at least two motor compressor units having motor and compression cylinders and with reciprocating pairs of pistons in said. cylinders, said units being arranged side by side with the axes of their cylinders parallel, and rods connecting the I pistons of the two units, so arranged that the connecting means of the other-pair of pistons,

and gear means engaged by both said racks.

24. In a motor compressor consisting of at least two motor compressor units each having motor and compressor pistons and motor and compressor cylinders, means connecting said units in such a manner that the working stroke of the motor part of one of the units both moves its own compressor piston and simultaneously causes the compression stroke of the motor piston and the suction stroke of the compressor of the other unit, means connected to the compression cylinder of at least one of said units to conduct the compressed air away from said last named cylinder, means in said conducting means operated when the pressure therein exceeds a predetermined amount to connect said conducting means to a space in which the pressure is lower than said predetermined amount, means to supply fuel to the motor cylinders, and means controlled by the pressure in said conducting means to reduce the feed of fuel to at least one of said motor cylinders as the pressure in said conducting means decreases.

25. In a motor compressor consisting of at least two motor compressor units each having motor and compressor pistons and motor and compressor cylinders, means connecting said units in such a manner that the working stroke of the motor part of one of the units both moves its own compressor piston and simultaneously causes the compression stroke of the motor piston and the suction stroke of the compressor of the other unit, means connected to the compression cylinder of one of said units to conduct the compressed air away of said last named cylinder, means in. said conducting means operated when the pressure therein exceeds a predetermined amount to connect said conducting means to a space in which the pressure is lower than said predetermined amount, means to supply fuel to the motor cylinder, means controlled by the pressure in said conducting means to reduce the feed of fuel to the motor cylinder of such unit as the pressure in said conducting means decreases, means connected to the compression cylinder of the other unit to conduct away the compressed air, said second conducting means being connected to said first conducting means at a point beyond said pressure operated means, means controlled by the pressure in said second conducting means to control the feed of fuel to'the motor cylinder of the second unit, whereby said second unit can function as a motor compressor when the motor piston and the motor cylinder of the first unit therefor act as a compensating cushion.

' 26. In a motor compressor consisting of at least two motor compressor units each having motor and compressor pistons and motor and compressor cylinders, means connecting said units in such a manner that the working stroke of the motor part of one of the units both moves its own compressor piston and simultaneously causes the compression stroke of the motor piston and'the suction stroke of the compressor of the other unit, means-connected to the compression cylinder of one of-said units to conduct the compressed air away from said last named cylinder, means in said conducting means operated when the pressure'therein exceeds a predetermined amount to' connect said conducting means to a space in which the pressure is lower than said predetermined amount, means to supply fuel to the motor cylinder, means controlled by the pressure in said conducting means to reduce the feed of fuel'to the motor cylinder of such, unit as the pressure in said conducting means decreases, means connected to the compression cylinder of the other unit to conduct the compressed air away, said second conducting means being connected to said first conducting means at a point beyond said pressure operated means, means controlled by the pressure in said second conducting means to control the feed of fuel to the motor cylinder of the second unit, whereby said second unit can function as a motor compressor when the motor piston andrthe motor cylinder of the first unit, therefor act as a compensating cushion, said last control means increasing the feed of fuel as the pressure increases up to the pressure at which said first unit idles and then decreasing the feed of fuel as the pressure increases further, causing the second unit to idle when the predetermined maximum pressure is reached.

27. In combination with a motor compressor consisting of at least two motor compressor units each having motor and compressor pistons, motor and compressor cylinders and means connecting said units in such a manner that the working stroke of the motor part of one of the units both moves its own compressor piston and simultaneously causes the compression stroke of the motor piston and the suction stroke of the compressor of the other unit, an engine driven by the air compressed by said motor compressor, means to conduct compressed air from said motor compressor to said engine, means to regulate the speed of said engine including means controlled by the speed of the engine to control the fiow of air through said conducting means, said control means reducting the pressure of the air as the speed of the engine decreases, means to supply fuel to. the motor compressor, and means controlled by the pressure in said conducting means to reduce the feed of fuel as the pressure in the conducting means decreases.

- 28. In combination with a'motor compressor consisting of at least two motor compressor units each having motor and compressor pistons, motor and compressor cylinders and means connecting said units in such a manner that the working stroke of the motor part of one of the units both moves its own compression piston and simultaneously causes the compression stroke of the motor piston and the suction stroke of the compressor of the other unit, an engine driven by the air compressed by said motor compressor, means to conduct compressed air from said motor compressor to said engine, means to regulate the speed of said engine including means controlled by the speed of the engine to control the flow of air through said conducting means, said control means reducing the pressure of the air as the speed of the engine decreases, means to supply fuel to the motor compressor, and means controlled by the pressure in said conducting means to reduce the feed of fuel as the pressure in the conducting means decreases, said engine comprising a turbine having a plurality of stages, said control means comprising means to direct the air to successively lower stages of the turbine as the speed of the turbine increases.

29. In a motor compressor consisting of at least two motor compressor units each having motor and compressor pistons, means connecting said units in such a manner that the working stroke of the motor part of one of the units both moves its own compressor piston and simultaneously causes the compression stroke of the motor piston and the suction stroke of the compressor of the other unit, the diameter and the dead spaces of the compressor cylinders being such that the sum of the motor energy of the one unit and the energy of the compressor cushion of the other unit decreases when the stroke of the pistons reaches their greatest permissible value, while the said sum increases when the stroke of said pistons reaches their smallest permissible value.

30. A motor compressor of the type described comprising in combination two power cylinders outer ends of the pistons of said first mentioned cylinders respectively, and rigid linkiess means for connecting one piston of one pair to the opposite piston of the other pair.

RAUL PATERAS PESCARA. 

